Means for automatically modifying the functioning of mechanical movements in sound-on-film motion picture apparatus



Jan. 29, 1935. L. DAY 1,989,166

MEANS FOR AUTOMATICALLY MODIFYING THE FUNCTIONING OF MECHANICALMOVEMENTS IN SOUND-ON-FILM MOTION PICTURE APPARATUS 8 Sheets-Sheet 1Filed Aug. l4, 1930 FIG./

INVENTOR 1,989,166 HANICAL Jan. 29, 1935. L. DAY MEANS FOR AUTOMATICALLYMODIF YING THE FUNCTIONING OF MEG MOVEMENTS IN SOUND-ON-FILM MOTIONPICTURE APPARATUS Filed Aug. 14, 1930 8 Sheets-Sheet 2 Jan. 29, 1935. Q

L. DAY MEANS FOR AUTOMATICALLY MODIFYING THE FUNCTIONING OF MEG HANICALMOVEMENTS IN SOUND-ON-FILM MOTION PICTURE APPARATUS 8 Sheets-Sheet 3Filed Aug. 14, 1930 INVENTOR ATTORNEY Jan. 29, 1935. DAY 1,989,166

Lv MEANS FOR AUTOMATICALLY MODIFYING THE FUNCTIONING OF MECHANICALMOVEMENTS IN SOUND-ON-FILM MOTION PICTURE .APPARATUS Filed Aug. 14, 19308 Sheets-Sheet 4 I II] INVENTOR 1,989,166 OF MECHANICA PPARATUS Jan. 29,1935. L. DAY

IF'YING THE FUNCTIONING MEANS FOR AUTOMATICALLY MOD L MOVEMENTS IN SOUNDON-FILM MOTION PICTURE A .Flled Aug. 14, 1930 8 Sheets-Sheet 5 S atINVENTOR lllll I QQR Jan. 29, 1935. L. DAY 1,989,166

FYING THE FUNCTIONING OF MECHANICAL FILM MOTION ARATUS Filed Aug. 14,1950 8 Sheets-Sheet 6 PICTURE APP MEANS FOR AUTOMATICALLY MODI MOVEMENTSIN SOUND-ON R O T N E V m Jan. 29, 1935.

L. DAY 1,989,166 MEANS FOR AUTOMATICALLY MODIFYING THE FUNCTIONING OFMECHANICAL MOVEMENTS IN SOUN-DONFILM MOTION PICTURE APPARATUS Filed Aug.14, 1930 8 Sheets-Sheet 7 INVENTOR Jan. 29, 1935.

MEANS FOR AUTOMATICALLY MODI MOVEMENTS IN SOUND-ON L. DAY 1,989,166FYING THE FUNCTIONING OF MECHANICAL -FILM MOTION PICTURE APPARATUS 8Sheets-Sheet 8 Filed Aug. 14, 1930 I 'IIIIIIIIIIIIIIII I Patented Jan.29, 1935 UNITED "STATES PATENT OFFICE MEANS FOR AUTOMATICALLY MODIFYINGTHE FUNCTIONING OF MECHANICAL MOVEMENTS IN SOUND-ON-FILM MOTION PICTUREAPPARATUS Leonard Day, New York, N. Y.

Application August 14, 1930, Serial No. 475,287

Claims.

understood that'any designation thereof in connection with projectors isnot intended to be a limitation to projectors. A clearer understandingof the invention will be had by describing it in connection withprojectors.

One object of the invention is to efiect the necessary movements of afilm for the showing of motion pictures and for the production of soundfrom the film in an improved manner both for the picture projection andfor the soundv production and while maintaining a desirable coordinationbetween these two functionings.

A further object of the invention in addition to the above is toemploy aGeneva cross so coordinated with the invention as to retain theaforesaid first mentioned object.

In carrying out the invention, an objective is to modify in a'i'avorablemanner the variables in the equation posed both upon an intermittentlymoving film efi'ecting the intermittent movewhich the framing device islocated in the oil and the parts for meat.

A further object of the invention is to coordinate forces both positiveand negative with time and with means for storing and/or absorbing forceto effect the general first mentioned object of the invention.

In other language, it is an objective to maintain continuous motion atabsolutely uniform speed for the portion of the film from which thesound is being produced; to provide a movement for another portion ofthe film step by stepior the respective pictures whereby each successivepicture is successively moved into the same position for purposes ofprojection where it is retained at rest and with the provision that itis obscured against projection during its actual shitting motion, allwith as great freedom from unnecessary To the extent to whichacceleration, either positive or negative, as -possible.

A further object of the invention is to improve sound-on-film sound andpicture projectors.

Th above and further objects of the invention will be particularizedmore individually in the claims which are directed to illustrativeembodiments of the invention solely for purposes of illustration and notlimitation. These embodiments of the invention are described in thefollowing specification in connection with the accompanying drawingswhich form a part hereof.

Fig. 1 is a cross-section with parts shown in elevation and with partsbroken away showing the intermittent and framing mechanism constructedin one form in accordance with my invention; Fig. 2 is a section drawnto an enlarged scale at right angles to Fig. 1 showing an improved formfor the framing mechanism; Fig. 3 corresponds to the right hand portionof Fig. l but shows the construction of Fig. 2; Fig. 4 is an elevationof the shaft of Figs. 2 and 3; Fig. 5 is an elevation partly in sectionand with parts broken away to show the interior of the sleeve of Figs. 2and 3; Fig. 6 is a cross-section of the sprocket forming a part of theassemblage of Figs. 2 and 3; Fig. 7 is a diagrammatic showing of theGeneva cross functioning in cooperation in theinvention; Fig. 8 is across-sectional view partly in elevation and corresponding to Fig. 3 butshowing a modification in which the torsion spring is supplanted by acompression spring working through a cam; Fig. 9 is a view similar toFig. 8 of a similar construction but one in which the cam-sleeves are,supplanted by reversely acting rifled sleeves; Fig. 10 is a viewcorresponding to Fig. 1 showing a modification incase instead of withinthe hub 01' the intermittent sprocket; Fig. 11 is a cross-sectional viewcorresponding to Fig. 10 but with parts broken away and parts when inelevation and indicating means in addition to those shown in Fig. 10whereby .framing is possible fromthe right hand of the structure asshown in the figure; Fig. 12 is a view similar to that oi Fig. 11showing means by which framing by manipulation from the same locality isaccomplished by means of torsion instead of tension as is the case withthe mechanism of Fig. 11; Fig. 13is a diagrammatic assembly view showingthe relation of the cooperative moving parts in a complete projector forsound and pictures; Fig. 14 is a view of a hydraulic governor which maybe substitutedfor the fly-wheel or friction brake of Fig. 13; l

Fig. 15 is a detail drawn to a reduced scale of a modification of thestructure shown at the left of Fig. 10 for the purpose of manipulatingthe framing at a different locality; Fig. 16 is a View of the same partsviewed from the left of Fig. 15; Fig. 17 is a front elevation of acomplete projector embodying many of the features of the invention, therelative positioning of the parts of which is not'a part of thisinvention; Fig. 18 is a diagrammatic view of a modification showing apreferred form of the flexible coupling for use in this invention; Fig.19 is a diagrammatic representation of the combined shutter and safetygate; and Fig. 20 is a section through a plane corresponding to theoperating pins at right angles to the plane of Fig. 19 and with partsbroken away and some omitted.

Although the Geneva cross shown in Fig. 7 is a mechanical movement, insome respects beautiful for the purpose'of effecting the intermittentshifting of film F, it has an outstanding disadvantage or defect. Thepin 1 has heretofore been understood to revolve at uniform speed aboutthe shaft or axle 2 and to be in functioning engagement with the cross 3in one of the slots 4 throughout about one-fourth of its revolutionduring which time the segmental flange 5 is out of locking engagementwith the arcuate faces 6. As an inherent quality of the Geneva cross,the angular velocity and the tangential velocity of pin 1 are constantwhereas the radius of application about the axis of rotation 7 of thecross of pin 1 tending to effect both positive and negative accelerationof the cross 3 varies from a long radius whenpositioned in the end ofnotch 4 to a very short radius when positioned in the bottom of notch 4.As a consequence, the speed curve for angular velocities or angularacceleration of the cross 3 is such that tremendous velocity is attainedthroughout a short portion of the revolution of pin 1 attended bytremendous positive and negative accelerations. This high speed and highacceleration manifestation occupies in the neighborhood ofone-thirty-second of one revolution of the pin 1. (The speed inacceleration curves for the four faced Geneva cross is well known. Seepp. 15 to 19 of Der Kinematograph und Das Sich Bewegende Bil by Dr. CarlForch.) Under the general object of the invention this limitation of theworking space or period for pin 1 is undesirable and to be overcome andI have accom plished it by simple mechanism.

Referring now more particularly to Fig. 1, the drive shaft for pin 1 ismechanically disconnected from shaft 8 which is shown receiving thedriving force from aprime mover as by means of belt 9, the effort ofwhich is stored in the form of momentum preferably in a fiy-wheel 10. Itis from this shaft 8 that the other moving parts of the apparatus aredriven as by gears -11 and 12. Between the shaft 2 and the shaft 8 isinterposed a resilient cushion coupling 13 as. shown in Fig.

' 1 and 13' as shown in Fig. 13. In the construc-' tion of Fig. 1, a huband flange 14 is fixed to shaft 8 and a similar hub and flange 15 isfixed to shaft 2 and intermediate disc 16 of resilient material such asleather is riveted at three points to the flange 14 and at threeintermediate points to the flange 15. In the construction '13, anH-shaped plate of resilient metal is seated in opposed end notches inthe shafts 8 and 2. The resilience and strength of the coupling 13 or 13is of importance. Its coordination with the Geneva cross and its ownquality of adjustment should be such that when the pin 1 meets with asubstantial 9995- ing force, it is permitted to slow down in itstangential speed in its own orbit and permit the force or torque fromshaft 8 to be stored in the form of distortion or strain in itsresilient part, the shaft 8 continuing its rotation at substantiallyunvarying angular speed. This storing of energy in the form of strain ineifect lengthens the time or the angle of rotation of shaft 8; duringwhich the pin 1 is exerting apractical degree of force upon the cross 3.It is unnecessary for the cross 3 first to attain a terrific speed froma terrific positive acceleration and then be accelerated by means of areverse force fromthe pin 1. The momentum stored by the shaft exertionof pin 1 is spread out not only during the time of tensing or strainingthe resilient part 16 but afterwards and during the time that the Genevacross usually functions under extreme de-acceleration. Thus, the cushioncoupling first is stressed to effeet a strain in the direction thatallows the shaft 8 to rotate more than the pin 1 is revolved, and inaddition, this moderate force from the pin 1 is harnessed to continuethe rotative urge upon the cross 3 beyond the time when de-accelerationheretofore had commenced and is even effective in permitting a slightover-riding of the pin 1 beyond the rotation of shaft 8 during theprocess of tie-accelerating the cross 3. An inspection of Fig. 7 willshow that both on entering and on leaving one of the notches 4, thetravel of the pin 1 is substantially tangential to the, faces of thenotch 4 at which locality the resilience tending to force the pin 1 toits normal position with reference to shaft 8 is efiective, there beingno component of force from the contacting surfaces of a notch 4 in thedirectionof travel of the pin the flange 5 and it is this fixed positionwhich is of importance in positioning the projected picture in theactual time, within minutes, of a revolution of the pin 1, when thisfixing takes place. The shutter mechanism functioning to obscure theprojection during the intervals of shift and to expose the image on thefilm during the positions of rest is geared to shaft 8, and even thoughthe phasing or timing of the periods of shut-oi! and exposure vary fiveor six degrees of a rotation of shaft 8', the only way this would bedemon- J strated would be in a variation of the illumination on theprojection screen, the film actually having been brought to rest in thesame position for each frame or picture and locked there. When oneconsiders that the force from the pin 1 necessary to effect a movementof the cross 3 varies with the square of the speed of cross 3 and thismeans with the square of its angular velocity, it becomes quite evidentthat the spreading out or lengthen ing of the time or angle throughoutwhich this force is functioning results in a great reduction in" themaximum force exerted at any time, a reduction in the maximum speed ofwhich the cross 3 moves at any time, and a great reduction in theacceleration for the cross both positive and negative. This tends toincrease the life of the cross as a mechanical movement and reduces thenoise of the machine and increases the life of the film.

In the mechanism illustrated in Fig. 1, the shocks of the engagements ofpin 1 are also shielded from the gear train 11, 12, etc. employed tomove other parts.

.I have not been satisfied with the modification of the variables in theequation by the alteration or change in the functioning of the pin 1 buthave also interposed between the shaft 3 and the film'F a second ortandem resilient relief. The shaft 7 of the cross 3 is resilientlyconnected to the intermittent sprocket 17 by means of aresilient-coupling 18 whereby if the pin 1 effects an acceleration ofshaft 7 beyond the capability of the force of resilient coupling 18 toeffect an instantaneous response in the form of a rotation of sprocket17, a temporary strain stores the force. in the coupling 18 and extendsits time of application to effect the required rotation of sprocket 17,which, however, is positively stopped with micrometer accuracy ofadjustment by the angular positioning mechanism A shown in Fig. l, orits various modifica- 8, I have effectively reduced the forces embodiedand applied by the pin 1 to the fourth power of the speed reduction atintermittent sprockets 17. As a matter of fact, I desire it to beunderstood either the relief as by the resilient coupling '18 working incooperation with a positive angular positioning device, or. the simpleresilient coupling 13, may alone be sufficient to transform the oldGeneva cross into one functioning so gently as to handle wide film suchas sixty-five millimeter film without injury. In the mechanismsillustrated these two resilient relief means are shown in tandem orcooperative. So far as the use of the relief means 13 isconcerned byitself it is to be understood that it need not of necessity be usedeither with the framing device shown in the figures or with the tandemresilient relief means 18. Again, it is to be understoodthat the framingmechanism of the invention may be employed together with the resilientcoupling 18 but assembled in the reverse sense so that the drive fromshaft 7 to sprocket 17 "is directly through the cam-sleeves with thespring mechanism 18 functioning to hold the parts in angular adjustment.

An oil box B having a flange 20 is adapted to be mounted upon the mainpanel of the projector with its interior 21 filled with a suitablelubricating oil. Suitable bearings are provided for the shaft 2, theybeing indicated by the numerals 22 and 23. The sprocket shaft'7 ismounted in bear.- ing 24 and between two end thrust bearings 25 and 26which are preferably ball bearings. 25 is adjustable in the cover plate27 and 26 is adjustable by a turn of theneweled grip 28 to rotate thethreaded stem 29 having threaded engagement in the out-rigger bracket 30mounted on the box B.

The hub 31 of sprocket 17 is slightly larger than the tubular shaft7-sufficiently larger to accomm0date with a bearing engagementtherebetween the cam-sleeve 32 which terminates at the right in Fig., 1'in a hardened steel cap 33, itself preferleft hand end of hub 31 isthreaded to the externally threaded nipple sleeve 36. A symmetricalnipple sleeve 37 is keyed or otherwise suitably fixed to shaft 7. Thesurfaces of these nipple sleeves 36 and 37 are tapered spiral groovedcombs 38 and 39 which engage and screw into opposite ends of a. spiralspring 40 of uniform convolutions. In assembling the structure, thenipple sleeve 37 is rotated in the direction of the arrow shown at theleft of shaft 7 so that the severed end 42 of the spiral spring ridesthe surface of nipple sleeve 38 preferably until a positive abutment isreached and the threads engaging with the hub 31 are of a directiontending to be tightened by this movement. At the same time, the nipplesleeve 37 rides into the other end of the spring 40 until the severedend 43 reaches an abutment or a sufficient enlargement of the nip-- pleso that further threaded engagement can not take place. An initialnormal set is then given to the spring 40 tending to unwind or expand itand the set screw or key fastening sleeve- 37 to shaft 7 is set orlocked. The rotative urge of spring 40 upon hub 31 relatively to shaft 7is such that cam-follower 50 fixed to the hub 31 is caused to engage thecamway 35. The camway being forty-five degrees both'to the circumferenceof the shaft and axial length of the shaft, exerts a force having anaxial component and a circumferential component. The axial component isto the right in Fig. 1 and is resisted by the engagement of bearing 26with cap 33. The circumferential component tends to rotate sleeve A inthe direction of the arrow in the left of the figure forcing earn-face34 into a 45 engagement with cam-follower 51 fixed in shaft 7. This camforce or cam follower 51.being at 45 has two components, one axial ofshaft 7 and the other circumferential of shaft 7. The axial component istowards the left in Fig; 1 and is resisted completely by hearing 25.The, circumferential component is in the direction of the arrow at theleft of Fig. 1, but having originated from the resilient set of spring40, the fixed end of which is fixed to shaft 7, produces nothing but anegligible strain in the mechanical assemblage.

It is thus apparent that a quick rotative efiort exerted by shaft 7 inthe direction of the arrow at the left of the figure, if quick enough,tends to. cause cam-follower 51 to rotate away from cam-face 34, andthis rotation of shaft 7, sleeve I Of course, it is to be understood andas out.previously,- the cam-followers and 51 may be reversed, that is,51 may be mounted upon the hub 31 and 50 mounted upon the shaft 7 andthe resilient coupling of spring 40 may be reversed from that indicatedin which case the drive from shaft 7 is unyieldingly imparted to thesprocket 17 through the cam-followers, camfaces and sleeve A ail theaxial components of the forces involved in the cams and cam-followersbeing taken up by the thrust bearings 26. In both cases, whether thedrive from shaft 7 to sprocket 17 is through the cushion of spring 40 orpositive through the cams and cam-followers, an axial movement of thebearing 26 is effective in changing the relative angular positionbetween sprocket 17 and shaft .7. In both cases the spring 40 tends totake up slack or lost motion and'to maintain the cams and camfollowersin engagement.

If the screw 29.is screwed in, the sleeve A is forced to the left andthe camways 34 and 35 movement opposite to the direction of the arrow atthe left of the figure so that the cam-followers 50 and 51 are no longerdiametrically opposite each other as shown in Fig. 1, but may be rotateduntil they actually contact one with another.

An unscrewing of screw 29, that is a lefthanded rotation, permits theurge of the spring 40 and the urge of the spring 36 to effect a shift ofthe sleeve A to the right, the camways 34 and 35 riding in engagementwith the cam-followers 51 and 50. This adjustment may take place toeffect the opposite angular movement between sprocket l7 and shaft 7until the camfollowers 51 and 50 engage each other on the faces oppositeto those previously engaged. By a movement of the sleeve A between itstwo extreme positions, a relative rotation between shaft 7 and sprocket17 of three-quarters of a complete rotation is easily effected. Thismeans three frames for the film F, four frames corresponding to acomplete circumference of the sprocket 17 in the figure. In practice itis seldom necessary to-effect a framing adjustment of more than half aframe in one direction or another, which means one-sixth of the totalframing adjustability of the framing mechanism described. It is well toset the spring 40 with sumcient rotative effort to make the reversemovement between sprocket 17 and shaft 7 throughout the completetraverse of the camways.

In Fig. 1, the shaft 7 is hollow and is provided with a port 53 openingwithin the hub 31 for lubricating the camways and other, parts and ,54for lubricating the thrust bearing.

thebearing cap 33 is provided with a perforation Itis preferred that thehub 31 have a flared portion 55 positioned within the oil catchershell-56 which may be mounted upon the boss 57 and is preferand51.are'substituted by rifling.

.associated therewith.

ably a shell of revolution. The exit duct 58 may be used to lubricatelower positioned bearings or may be returned to the chamber 21.

It is contemplated that an automatic oil supply for theinterior 21 ofthe case B may be Figures 2, 3, 4, 5 and 6 s J Figures 2, 3, 4, 5 and 6show a modification of the same general construction shown in Fig.

female threads or rifling l34 which takes the place of the cam 34. Thesetwo parts fit with a good bearing fit upon the outer and inner faces 101and 102 of the rifling, but with a little lost motion along the sideedges 103 and 104 of the rifling. This is useful in providing a shockslack to enable the spring 18 to function. The exterior of sleeve 132 islikewise provided with rifling or threads 135 which take the place ofthe cam 35 and mesh with and cooperate with the internal rifling 150formed on the interior of the hub 131. Thus the hub bears snugly nestedabout sleeve 132 and sleeve :132bears snugly nested about shaft 7although there is preferably rotary play and axial play, between all therifiings, and it is preferred that the edges of the rifiings slightlytaper like a 2; thread so that when relative axial thrust or relativerotation is applied to the parts, all the outer nested parts will tendto maintain the same axis. This play is 'shownin exaggeration in Fig. 2.Although Fig. 2 shows a lack of contact between the circumferentialparts 7, 132 and 131, it is intended in practice that these partscontact with hearing fit, merely a suficient' looseness being providedto permit lubrication. The construction shown in these figures 2, 3, 4,5 and 6 is the best mechanicalconstruction for adjustment and shocktake-up within the sprocket, but was considered not so clear ofexplanation as the cam. and cam-follower construction. Its functioningis identical except, of course, that there is no localized cam-follower.struction all the parts are continuous cams or threads or rifiings andthe bearing surfaces are so extensive that no appreciable loosenessexists In this preferred con-.

and'lubrication is efficient. It is preferred that the pitch of therifling be approximately 45 or, in other words, so that the rotativeeffect may be brought about with equal case either in responsethe shaft7 is extended all the way through the hollow hub 232 of the sprocket towhich it is secured by pins 111. Instead of the shaft 7 bearing directlyin the houseB, the sleeve 112 mounting the spring 18 works in thebearing 113 and forms a bearing for the sha t 7. The Geneva cross proper114 is fixed to the leeve 112, the inner end of which is threaded bythreads 115 to mount the internally rifled sleeve 116. This sleeve fitsthe external rifling 117 of the intermediate sleeve 118, which in turnis rifled to mesh with the riflin 119 on the left hand end of shaft 7.An assembly maintaining spring 120 is'provided and a bearing cone 121 tocooperate with the ball bearing 122 which is adjustably mounted on screw123 operable by thumb boss 124 external. to the cas-' ing B. In thisconstruction the right handball bearing 125 inv out-rigger bracket 126reacts a ainst adjustable ball bearing 122 so that a van ment forframing is shown localized at a position operated fromthe rear of thefilm compartment, namely, in a position usually at the rear of theprojector. If desired, instead of the knurled finger wheel 124, thescrew 123 may be operated by the worm gear 142 operated by the worm 143fitted on shaft 144 which in turn is operable by a knurled wheel 145which may be located outside of the frame of the machine at anyconvenient locality either to the right or the left.

In Fig. 11 another modification is shown for the application of thefinger manipulation to effect framing. In this figure it is understoodthat the general construction is that of Fig. 10 but that the shaft 7 isprovided with a central bore 700 to accommodate a through-tension bolt160. The tension bolt is pulled or relaxed by the finger wheel havingthreaded engagement with the threaded end 161. The left end of-thistension rod is fixed as by tight threads 162 or a pin in thenon-rotating stub end 163 of bearing 122. Suitable means such as thespline 164 should be provided to prevent the rotation of this bearingpart in the chamber wall 165. In this construction it is expedient thatthe relative size of the tension bolt and the bore 700 be such thatthetension bolt does not contact with any part of the shaft 7 to exertfriction thereon.

In Fig. 12 another modification is shown in which a torsion shaft 260replaces the tension shaft 160. In this construction the right end ofthe'shaft is fixed to a finger wheel 261 and the left end of the shaftis provided with a non-circular part 170 working in the complementaryshaped bore 171 in screw 1'72 which mounts the bearing 122. In thisconstruction likewise, it is necessary to prevent contact between theshaft '1 and the through-bolt 260., Obviously, a rotation of fingerwheel 261 effects a rotation of screw 172 in its threaded seat to effectthe same purpose as the manipulation of wheel 124 of i 10.

As set forth above, several methods of finger manipulation to effect theframing in accordance with the principal and general construction ofthis invention have been described and illustrated. It is to beunderstoodthat this finger manipulation may indeed be carried to almostany part of the projector or camera.

Although the preferred means and method for resisting or reactingagainst the finger manipulation to effect framing is the torsion spring18, which also may or may not provide the relief for the inertia of thesprocket, it is possible to eifect this reaction, in fact all of them,by means of a compression spring 180 as shown in Figs. 8 and 9. In thisconstruction, in addition to the double cam structure 34 and, 35cooperating with the cam-followers or pins 51 and 50, there is a secondreverse acting double cam 200 having the camway 234 and the camway 235.These are a part of a single sleeve 201, the complement to the sleeve 32and the camways work on the same pins or cam-followers 50 and 51. Allthese camways are preferably 45 to the circumference and are spiraled orwarped surfaces so that elemental line contact is maintained with thecam-followers 50 and 51. In this construction, the thrust of thecompression spring 180 translates itself partly into a rotativecomponentat the cam-followers so that a movement of the bearing 125 tothe right is followed up by this spring 180 and its operating cams.

In Fig. 8 the same modification for a thrust spring 180 is shown inconnection with two sets G and H of symmetrically formed rifled sleevessuch as those described in connection with Figs. 2, 3, 4, 5 and 6. Theset G work in the opposite sense to the set H just as the double set ofcams work in the opposite sense in Fig. 8.

In Fig. 13 there is a diagrammatic assembly of a motion pictureprojector mechanism including means for sound on film reproduction shownwith particular regard to the mechanical movements and their automaticcontrol in accordance with the present invention. Any suitable primemover such as the motor 300 serves to drive the apparatus as by a belt301 working upon the combined pulley and fiy wheel 302. It shouldparticularly be noted in connection with this construction that the fiywheel is not fixed to the shaft 2 carrying the pin wheel and driving pin1 of the Geneva cross construction. of course the fiy wheel may beseparate from the pulley. It is preferred that this shaft 2 have its ownseparate bearings one at each end and that it be mechanically a separatepart from the shaft 8 initially receiving the power and steadied withits attached 'fiy wheel. Any suitable form 1'- of fiexible coupling suchas the coupling 13 resiliently connects the shaft 8 to the shaft 2. Itis preferred, however, that a limiting stop mechanism of positivecharacter such 'as the eye and pin construction 304* be employed so thatin the event of an improper adjustment of resilience for the part 13 anultimate limit be set upon the cushioning relative movement between therotation of shaft 8 and shaft. 2.

J indicates any one of the framing cushioning sprocket constructionspreviously described in connection with Figs. 1, 2, 3, 4, 5, 6, 7, 8, 9and 10. 310 indicates any suitable form of shutter properly time gearedto thesprocket mechanism J so that the light is obscured during theinstant of film shift and is projected through the film at the times ofrest. It should, however, be noted that there is not a positive timingbetween this sprocket and the shutter. In other words, the fiexiblecoupling 13 and the flexibility of the film shifting sprocket isinterposed between the gearing which does the fixing. It is well to timea shutter of this character slightly differently than is an ordinary onetimed. It is best to allow for the time lag occasioned by the tworesiliences working in tandem if both resiliences are employed, or forone if only one is employed. Also the timing may be the ordinary if theresilient relief is limited to the normal time of pin engagement in thecross. This means the shutter 310 should close and open a little laterthan the actual gearing would indicate. One of the important features ofthis invention is the fact that ,what has heretofore been considered tobe inherent substantially instantaneous action of the Geneva cross nolonger need be tolerated. It is remarkable how the normal accelerationand speed curves of the Geneva cross are modified even by the resilientcoupling 13 alone without in any way interfering with the timing of theshift and still periods for the film. The film, instead of movingsubstantially instantaneously with a tremendous tearing jerk, utilizespractically the full period of shut-off to move with a gentle positiveand negative acceleration. With my mechanism, it is possible to speed upthe negative acceleration which really takes place automatically onaccount of the resilient snap ahead of the coupling 13 as well as thespring 18 if that is employed. The reason negative acceleration may bevery rapid is because this is merely effective in allowing the film tostop and is not jerking it against the friction of the film gate.

Continuing in connection with Fig. 13, it is preferred that after theGeneva cross sprocket only spring seated holding roller 321.

" of maintaining a constant retarding effort for any given speed but ofopposing a retarding force to a speed at least in proportion to thesquare of the speed but, in accordance with some authorities, morenearly in accordance with the cube of the speed.

Next following the braked roller 320 is an ed e position roller 330.This roller is not driven but is accurately mounted in bearings fixedagainst end-wobble or wobble of any kind. The surface 331 of this idleris tapered away from the beveled flange 332 so that in accordance withthe principle of belts and pulleys the film F tends to ride out againstthe flange 332 which serves as a fixation or fixing guide automaticallyto determine the position of the sound track 333 of the moving film Frelatively to the sound opening or sound gate 334. No other fixation isnecessary. Beyond the sound gate 335 is the continuous motion draggingsprocket 336. It is this sprocket which it is desirable to drive at asnearly uniform speed as possible and to this end it should be fittedwith a fiy wheel 33'? and should not be a partof the drive shaft 338which should be coupled to it by means of any suitable resilientcoupling such as the resilient coupling 13'. In

,connecion with this coupling it is particularly expedient that somelimiting device such as the eye' and pin construction 304 be employedalthough it is preferred that a construction like that shown in Fig. 18be employed.

In Fig. 18 the rotating part to be driven is indicated by 337 and therotating driving part by ly positioned connect these parts.

340. Tension springs 341 diametrically opposed- Mid-positioned betweenthe springs 341 are inextensible slack links 342 which may take the formof chains fixed at their ends to the pins 343 and 344. In thisconstruction, on starting and stopping, the chains supply the torque.When the apparatus has gotton-to speed, the springs 341 adjust the partsto an intermediate position with the inextensible links slack so that abeautiful cushioning effect takes place. The lead of the part 340 overthe part 337 determines the driving tension which varies from zeroautomatically up to enough to drag the film. Beyond the sprocket 336 ispreferably a hold-back sprocket resisting the wind-up reel.

The fiutter or irregularity of film motion due I to the engagement ofthe teeth of sprocket 336 in' the film perforations is all taken up bythe .inertialess laterally deflecting springs 400 of the plifier withinthe structure, the shutter mechanism and the other parts describedherein in detail. Although there is shown in the figure a sprocket 400following the framing sprocket and just preceding the antiweaving idler330, it is not to be understood that this is preferred. In fact,

a curved or any standard film gate of the type having spring pressedsleds like that indicated by 500 which guides the-film F and at the sametime retards it as it is fed to the sound gate is the preferredconstruction, it is being understood, however, that sprocket, roller orsled guide are all better than a gear driven sprocket, the roller andthe idler sprocket being subjected to frictional retard either hydraulicor otherwise. It is preferable that no fiy wheel be provided on thispart. 7

To permit the local mounting of the microphonic parts of the amplifiermechanism, a platform 600 is provided preferably regular inconfiguration such as rectangular. The various mlcrophonic devices suchas the photoelectric cell 601 and the triode amplifier tubes 602, 603,have their sockets fitted to this platform. Attachments for eightsprings 604 are provided. Adjustable-counter weights 605 and .606, asmany as convenient or necessary, are rigidly secured to the platform600. so as to both substantially increase the mass of the entirestructure and in addition modify the mass distribution so that thecenter of gravity is the center of the points or attachment of thesprings 604. Each of these springs is extended out and fixed to aconvenient separated mounting support. 607. It is preferred that thedirection of each spring makes an angle of 45 with every dimension ofthe platform, that is, if the platform is rectangular, 45 with its planeand 45 with its edges. The springs are so adjusted that with theplatform horizontal the four lower springs substantially lose theirtension in response to the movement in response to gravity of theplatform. By this construction, if the force of one spring is K for anyposition of the platform, the supporting force for the entire platformis The force of the springs should be selected so that it is justsufficient to prevent the movement of the platform beyond a permissiblelimit for any position-rightside up, upside down, end-on or side-on. Itisnecessary that the tension of thesprings'be as slight as possible andthe mass of the platform with its mounted parts he as greatmass-spring-couple' be below audibility. As a matter of fact, with thisconstruction the platform with its tubes is usually slowly swingingwhich does not transfer any microphonic noise, the period being too slowand despite the fact that it is mounted within apparatus vibrating athigh speed, no microphonic noises are generated.

Although it is best that the center of gravity be mid-positioned, anapproach to that condition is valuable. The platform may be aparallelepiped with the springs at each corner.

In the construction shown, the fire gate is preferably embodied in themulti-part shutter 700 which is made up preferably of three shuttersspring urged to overlap openings and form virtually a closed disc whenthe machine stops, and inertia and centrifugal urged into juxtaposedposition when the machine starts, so as to operateas one shutter.

-as possible so that the vibratory period of the In Figs. 19 and 20there is shown in detail one embodiment of 'the combined inertian,spring and centrifugal controlled safety gate and shutter. In thisconstruction the drive-shaft 800 rotates, as viewed in Fig. 19,clockwise and is geared to time with the frames 1 of the film F and, ofcourse, with the mechanism intermittently shifting the film. In the.construction illustrated two balanced light interruptions take place,although the shift of the film from one frame tothe next is arranged andtimed to take place solely within one of the said light interruptionsOne shutter a, having diametrically opposite cut-offs a and a", andintermediate diametrically opposed light openings a and a" is riveted asby rivets b to the flange of hub d which, in turn, is fixed as by key eto shaft 800. In addition, two similar shutters or and on are providedin juxtaposed relation to shutter a but to'rotate freely upon shaft 800.They are shown respectively riveted to the free turning hubs g and hwith the assemblage held in axial position on shaft 800 by the set-screwcollar 1'.

- In Figs. 19 and 20 the construction 700 is shown with its parts intheir proper positions for non- -rotation in which the disc made up ofthe three parts a, a1 and a: functionsasa safety gate to prevent thepassage of light to the fllm. In this position the retrieving springs aand 7'1 function so that the shutter a1 is rotated clockwise a sixth ofa rotation relatively to shutter a and shutter a: has been rotatedone-third of a rotation relatively to shutter a and one-sixth of arotation relatively to shutter or, all these relative rotations beingclockwise as viewed in Fig. 19. Pivoted by rivet k to shutter a is aninertia centrifugal palet lever I, linked by pivotal link m to pin 11,which passes through the limiting arcuate notch-o in shutter 11- fromits rivet seat p in shutter or. In this position, the retrieving spring7 is holding the pin n against the limit of its clockwise travel innotch o. The limit of the travel of pin n in notch o in .acounterclockwise direction causes shutter 01 to juxtapose with itscut-off portions so as to coincide with the position of the'cut-offportions a and a of shutter a.

A pin n1 is seated by its rivet seat 111 to shutter a2. Pin m passesthrough an arcuate notch 01 in shutter a1, and has pivoted to it thefree end of link m1 and the free end of retrieving spring 7'1, all ofwhich parts operate in a manner similar to the similarly lettered partswithout subs but with relation to shutters a2 and or instead of withrelation to shutters a and or. The positioning of the palet lever 11might be one-sixth of a-rotation clockwise from the position of paletlever l, but it is shown one-half of a rotation plus one-sixth of arotation clockwise ahead of the position of palet lever. l. The purposeof this is to insure the diametrically opposite positioning of paletlevers l and 11 when the shutter is rotating so that the parts shall bebalanced about the shaft 800.

When the shaft 800 starts to rotate clockwise, it carries with itshutter a which is fixed thereto. The two other shutters a1 and a:byinertia tend to stand still.v Likewise the centers of mass of paletlevers l and Z1 tend to stand still. All of this inertia functioningtends to oppose the re-.

disc.

inertia functionings described above may be arranged to be nearlysufficient to bring the plurality of shutters into juxtaposition uponthe starting of the rotation of the shutter a and centrifugal force needbe employed solely to complete the relative motion and to hold the partsin the juxtaposed positions from the continuing centrifugal forcewhichis a function of the normal speed of rotation of the shutter. Itshould be noted that when the palet leversl and'lr swing radiallyoutward, the forces of tension and compression between the links and thepalet levers are close to dead center so that the centrifugal force hasan advantage in overcoming the tension of the retrieving springs and isamply sufllcient to hold the respective stop-pins n and m in thecounterclockwise limit of themeasuring notches o and 01 respectively.

Upon the stopping of the rotation of shaft 800 and its attached shuttera, obviously the other two shutters tend to continue to rotate, and thepalet levers l and Z1 tend to rotate from momentum about their pivots kand k1, so that there is inertia functioning 7' and 7'1 to snap the twomovable shutters or and a: clockwise relatively to shutter a to form aclosed disc.

- For purposes of simplicity, each cut-off portion of a shutter has beenillustrated as exactly one-sixth of the shutter or disc representedthereby. It is obvious that the main or shaftfixed shutter a mayconveniently have its cutoff portions a little more than a sixth so thatthe nicety of adiustment between pin n and notch o and between pin m and'notch 01 need not be so exact. Obviously, also, a shutter and safetygate of this type may be made up oLany reasonable number of shutters,the proportion of cut-off to opening determining-the number. Three issufficient when each cut-off is a sixth of the entire If the cut-offwere a third of .the entire disc, two cut-offs would be sufilcient.

An advantage of thepresent construction, be-

sides the certainty of its action, isthe fact that sity be mounted andshaped as they are shown.

If there is any advantage in having all the operating mechanism locatedinside the planes of the first and the last shutter instead of havingthe palet lever 1 outside of the first shutter, this may be done. Thismay be accomplished by reversing the sense of the palet levers and linksand fixing the 'pins alone in the outer shutter a.

What I claim and desire to secure by United States Letters Patent is: I

1. In a motion picture machine, a source of power rotation; a rotaryshutter geared thereto; aGneva cross combination having its crosssbaftand its pin-shaft; and a resilient coupling close to the pin wheel ofthe Geneva cross combination and between said pin-shaft and said sourceof power rotation, said resilient coupling serving to drive solely saidGeneva cross combination.

2. In a motion picture. machine of the intermittent fllm moving type, asource of power rotation; a rotary shutter geared thereto; 9. Genevacross combination including a slotted cross adapted to be rotated and tocome to rest intermittently, fitted with a sprocket shaft havingsuitable bearings and a cooperating pin wheel structure including inrigid assemblage a driving pin for engaging in the slotted cross; alocking ring and a journaled pin-shaft; a flywheel fixed to rotatevabout an axis aligned with the axis of said pin-shaft at uniform speedand intergeared withsaid shutter and said source of power rotation; acoupling resilient for both clock-wise and said pin without altering thetiming of the positions of rest for the cross.

' 3. In a motion picture machine of the intermittent film moving type, apower driven fly wheel having a journaled fly wheel shaft; a Genevacross assemblage including cross and cross-shaft and pin-shaft pin andlocking flange of integral construction, said pin-shaft being journaledin alignment with said fly wheel shaft; a resilient coupling saidpinvshaft to said fly wheel shaft of predetermined resilience tofunction in response to the force reaction between the pin and thecross.

4. In a motion picture machine of the intermittent film moving type, apower driven fly wheel having a journaled fly wheel shaft; 9. Genevacross assemblage including cross and cross-shaft and pin-shaft pin andlocking flange of integral construction, said pin-shaft being journaledin alignment with said fly wheel shaft; a resilient coupling couplingsaid pin-shaft to said fly wheel shaft of predetermined resilience tofunction in response to the force reaction be tween the pin and thecross; an intermittent film sprocket; and a resilient coupling betweensaid intermittent film sprocket and said cross-shaft.

5. In a motion picture machine of the inter? mittent type, a Genevacross assemblage including a journaled cross-shaft; an intermittent fllmsprocket having a hub surrounding said crossshaft; a sleeve constructionhaving sharp pitched threaded engagement with said hub and with saidcross-shaft; two spring means tending to take up lost motion betweensaid cross-shaft and said hub for both clockwise and counter-clockwiserelative rotations between said cross shaft and said intermittent filmsprocket; and means for ef-' fecting relative rotation between saidcross-shaft and said hub through the medium of said sleeve and whilesaid shaft. and said hub are both rotating.

LEONARD DAY.

CERTIFICATE OF CORRECTION.

Patent No. c989, 166. January 29, 1935.

- LEONARD DAY.

It is hereby certified that error appears in the printed specificationof the above numbered patent requiring correction as follows: Page 1,second column, line 5, for "Th" read The; and page 8, first column; line32, claim 3, before "said" first occurrence insert the word coupling;and that the said Letters Patent should be read with these correctionstherein that the same may conform to the record ofthe case in the PatentOffice.

Signed and sealed this 18th day of June, A. D. 1935.

Leslie Frazer (Seal) Acting Commissioner of Patents.

CERTIFICATE OF CORRECTION.

Patent No. 16 89,166. January 29, 1935.

- LEONARD DAY.

It is hereby certified that error appears in the printed specificationof the above numbered patent requiring correction as follows: Page 1,second column, line 5, for "Th" read The; and page 8, first column; line32, claim 3, before "said" first occurrence insert the word coupling;and that the said Letters Patent should be read with these correctionstherein that the same may conform to the record of the case in thePatent Office.

Signed and sealed this 18th day of June, A. D. 1935.

Les l ie Frazer (Seal) Acting Commissioner of Patents.

